Refrigerant compression scroll compressor

Abstract

To improve lubrication of a second swing bearing and lubrication of a peripheral frictional stress component.SOLUTION: A scroll compressor of the present invention includes a compressor housing, two scrolls, respective base plates, an eccentric drive, a drive shaft, a rotating shaft, a counterweight, a first bearing, a second bearing, and a counter pressure space. A sealing washer seals the first bearing on one side of a radially outer portion of an area between an inner ring and an outer ring through which fluid can flow, at the same time, a sealing washer is fixed to the first bearing at one side of the first bearing facing a cavity of the rotatable counterweight and a cavity of the second bearing such that the sealing washer is radially spaced from the inner ring to maintain a gap through which fluid can flow.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a scroll compressor for compressing refrigerants. The design of such a scroll compressor allows for an improved oil concentration and distribution system for lubricating bearings and frictionally stressed components within the scroll compressor. The present invention also relates to a method for oil concentration and distribution in such a scroll compressor. The present invention can be applied to electric refrigerant compressors for automotive air conditioning. [Background technology]

[0002] A scroll compressor has a compressor housing and two stacked scrolls, each with a base plate and a scroll-shaped wall extending from the front of the base plate. One of the two stacked scrolls is fixed, while the other can move eccentrically on a circular path. This movable scroll is also called an orbiting scroll. The movement of this scroll periodically changes the volume of the compression chamber formed between the scrolls, allowing refrigerant to be drawn in and compressed. The moving scroll moves on a circular path via an eccentric drive. The eccentric drive is formed by a drive shaft that rotates around its rotation axis and a counterweight that rotates with the drive shaft. The moving scroll is eccentrically connected to the drive shaft through the counterweight. That is, the axis of the moving scroll and the axis of the drive shaft are offset from each other. The moving scroll is supported by the counterweight through a second bearing, also called an orbiting bearing, while the drive shaft is supported by the compressor housing through a first bearing, particularly a ball bearing (also called a main bearing). Within the compressor housing, a so-called counter-pressure space is formed behind the base plate of the moving scroll. This counter-pressure space, also known as a counter-pressure chamber, is subjected to a pressure less than the outlet pressure (high pressure) but greater than the suction pressure (low pressure) of the substantially gaseous fluid being compressed. This counter-pressure serves to hold the moving scroll against the fixed scroll.

[0003] Scroll compressors also typically have a guide device that prevents the rotation of the moving scroll and allows it to circulate. The guide device is typically formed in a plurality of pocket-shaped receiving sections, each having a circular opening, on the rear surface of the base plate of the moving scroll. These receiving sections, also known as orbiting pockets, are arranged at a specific distance from each other and may be formed, for example, as closed holes. The guide device also has pins that protrude from the wall of the compressor housing and engage with one of the pocket-shaped receiving sections formed in the base plate of the moving scroll. Thus, a first end of the pin can protrude from the wall of the compressor housing, while a second end of the pin can be embedded in the wall of the compressor housing.

[0004] Due to the geometric design of the scroll compressor, there are many components in the counter-pressure space that are subject to frictional stress. Therefore, in addition to the first bearing (main bearing) and the second bearing (orbiting bearing), scroll compressors have other components that require sufficient lubrication in the circumferential direction, especially during high-speed operation, and are subject to frictional stress. Not only is the total amount of oil in the counter-pressure area related to the desired lubrication, but oil distribution is also important. Lubrication of the second orbiting bearing, which moves eccentrically and simultaneously rotates around its axis, is particularly challenging. Sufficient lubrication of the secondary bearing is essential to prevent bearing fatigue.

[0005] For example, relatively complex active oil returns are known from the state of the art, in which oil circulating in a circuit is supplied to the surrounding installation space of the second slewing bearing.

[0006] One possibility to balance the lubrication of the second bearing and surrounding frictional stress components is to fill the cavity of the rotating counterweight with oil. However, if the cavity of the rotating counterweight is completely filled with oil, the driving force required to operate the compressor increases. In this case, the counterweight must overcome the flow resistance of the liquid oil phase instead of the gas phase of the refrigerant.

[0007] The function of a scroll compressor primarily requires the return of gaseous refrigerant. Passive lubrication of the second orbiting bearing and surrounding frictional stress components by oil components in the refrigerant flow is also known. The rotational movement of the shaft and counterweight expels the oil necessary for lubricating the orbiting bearing and surrounding frictional stress components to the outside. In this way, the orbiting ball bearing and surrounding frictional stress components are located in an internal area where the refrigerant gas and oil mixture does not flow. The flow guide may result in oil vapor not flowing through the second orbiting ball bearing or surrounding frictional stress components and not providing them with sufficient lubrication. Therefore, the oil supply to the orbiting bearing cannot be guaranteed under all operating conditions, especially at high speeds. Summary of the Invention [Problem to be solved by the invention]

[0008] The object of the present invention is to improve the lubrication of the second slewing bearing and the surrounding friction stress components. [Means for solving the problem]

[0009] The object of the present invention is achieved by a scroll compressor for compressing refrigerants having the features of claim 1. Such a scroll compressor enables an oil concentration and distribution system and method. Such a system is particularly suitable for electric air conditioning compressors. Advantageous features are also described in the dependent claims.

[0010] According to one embodiment of the present invention, the scroll compressor includes a compressor housing, two scrolls stacked within the compressor housing and each having a base plate, and a scroll-shaped wall extending from a front surface of the base plate. One scroll is fixed and the other scroll is movable eccentrically along a circular path. By moving the scroll, the volume of a compression chamber formed between the scrolls can be periodically changed. Refrigerant is drawn in and compressed. The scroll compressor also includes a drive shaft rotatable about a rotation axis, and an eccentric drive rotatable together with the drive shaft, the drive shaft including a counterweight, the drive shaft eccentrically connecting the moving scroll to the drive shaft, and the scroll is movable along a circular path.

[0011] The scroll compressor includes a first bearing in the compressor housing that supports the drive shaft and a second bearing in the counterweight that supports the moving scroll. The scroll compressor also includes a counterpressure space in the compressor housing at the rear surface of the base plate of the moving scroll, in which a cavity for the rotatable counterweight and a cavity for the second bearing are formed. According to the present invention, a sealing washer is fixed to the first bearing at one side of the first bearing facing the cavity for the rotatable counterweight and the second bearing so that the sealing washer radially seals one side of the first bearing against the rotation shaft at the radial outside, i.e., the outer portion, of the region between the outer ring and the inner ring of the first bearing through which fluid can flow, and at the same time, the sealing washer is radially spaced from the inner ring so as to maintain a gap through which fluid can flow.

[0012] The sealing washer is preferably fixed to the outer ring of the first bearing through a clamping connection.

[0013] The sealing washer and the gap are both formed in a ring-shaped manner. This variant is advantageous in all embodiments where the first bearing is a rolling bearing, in particular a ball bearing having an outer ring, an inner ring, and rolling elements distributed around the entire circumference between them. A beneficial development of the invention is that a circumferential groove for fixing the sealing washer is formed in the inner wall of the outer ring of the first bearing to accommodate the sealing washer.

[0014] Typically, the second bearing is a rolling bearing, preferably a ball bearing, having an outer ring, an inner ring and rolling elements distributed all around the ring between them.

[0015] Another embodiment of the present invention relates to an oil concentration and distribution method for lubricating bearings and friction-stressed components of the scroll compressor described above, wherein during operation of the scroll compressor, a fluid mixture of refrigerant gas and oil flows into the counter-pressure space.

[0016] The oil separated from the fluid mixture by centrifugal force generated by the rotational flow of the refrigerant gas and oil mixture caused by the rotating counterweight is concentrated by the sealing washer acting as a barrier from the counterweight cavity and the second bearing cavity to setting an oil level sufficient to lubricate the second slewing bearing.

[0017] The core of the solution of the present invention is the first bearing, also known as the main bearing, which is partially sealed on one side by the seal washer. A radial gap is left open relative to the inner ring of the first bearing. The geometric design of the cavity of the counterweight and the resulting adaptation of the counterpressure space induce oil concentration within the cavity, ensuring sufficient oil distribution without loss due to splashing. The rotational flow within the cavity of the counterweight caused by the rotating peristaltic counterweight separates the oil from the multiphase mixture of the control mass flow from the valve, generating a specific radial oil level determined by the seal washer's measurement, for example, by its inner diameter, preferably in a ring-shaped form. In this case, the oil can concentrate until it reaches an oil level corresponding to the inner diameter of the ring-shaped seal washer. Therefore, the radial oil level corresponds to the set radial oil level due to the barrier effect of the seal washer, and the ring-shaped seal washer is used, with its inner diameter located between the radial outer ring of the second bearing and the inner ring of the second bearing. Particularly preferred is an embodiment in which the sealing washer has an inner diameter corresponding to the radial oil level setting as a result of the barrier effect of the sealing washer, and its horizontal plane is closer to the inner ring of the second bearing than to the outer ring. [Effects of the Invention]

[0018] The primary advantage of the present invention is a significant increase in fatigue strength of frictionally stressed components due to a larger and better distributed lubrication. Scroll compressors according to the present invention, having an improved system for oil concentration and distribution for lubricating bearings and other frictionally stressed components, have a longer life, are quieter, wear less, and are more efficient. Significantly less power loss can be achieved than with oil supply or oil return systems for lubricating bearings and frictionally stressed components in scroll compressors known to date. The present invention also allows for a complete reduction in oil volume, providing a cost-effective solution. [Brief explanation of the drawings]

[0019] Further details, features and advantages of embodiments of the present invention will become apparent from the following description of exemplary embodiments with reference to the associated drawings. [Figure 1] FIG. 2 is a vertical cross-sectional view of the scroll compressor. [Figure 2] FIG. 1 is a detailed view showing controlled mass flow and oil deposition in the counter-pressure space of a scroll compressor. [Figure 3] FIG. 10 is a diagram showing additional details of the control mass flow and oil deposition in the back pressure space of the scroll compressor. [Figure 4] FIG. 10 is a cross-sectional view of a first bearing with a sealing washer applied to one side. [Figure 5] 10 is a schematic diagram of oil condensation from the refrigerant and oil mixture in the counter pressure space when a sealing washer fixed to one side of the first bearing is applied. [Figure 6A] FIG. 2 is a perspective view of a first bearing. [Figure 6B] FIG. 1 is a perspective view of a first bearing with circumferential grooves in the outer ring of the bearing. [Figure 7] FIG. 10 is a perspective view of a drive shaft integrated into a compressor housing and supported by a first bearing, and a sealing washer before being fixed to the first bearing. [Figure 8]1 is a perspective view of a drive shaft supported by a first bearing, with a sealing washer integrated into the compressor housing and fixed to the first bearing; FIG. [Figure 9] FIG. 2 is a cross-sectional view of the scroll compressor in the plane of the sealing washer fixed to the first bearing. DETAILED DESCRIPTION OF THE INVENTION

[0020] FIG. 1 illustrates a longitudinal cross-sectional view of a scroll compressor (1) for compressing a refrigerant. While FIG. 1 illustrates the configuration of the scroll compressor (1), it does not show all of the features of the present invention and is primarily used for illustrating the present invention. The scroll compressor (1) includes a compressor housing (2), two scrolls (3, 4) stacked within the compressor housing (2) and having respective base plates (3a, 4a), and scroll-shaped walls (3b, 4b) extending from the front surfaces of the base plates (3a, 4a). Of the two stacked scrolls (3, 4), one scroll (3) is fixed, while the other scroll (4) is eccentrically movable along a circular path. This movable scroll (4) is also referred to as the orbiting scroll (4). The movement of the scroll (4) periodically changes the volume of the compression chamber (5) formed between the scrolls (3, 4). Refrigerant is drawn in and compressed. The moving scroll (4) moves along a circular path via an eccentric drive. The eccentric drive is formed by a drive shaft (6) that rotates about a rotation axis (7) and a counterweight (8) that rotates together with the drive shaft. The moving scroll (4) is eccentrically connected to the drive shaft (6) through the counterweight (8). That is, the axis (9) of the moving scroll (4) and the rotation axis (7) of the drive shaft (6) are arranged offset from each other. The moving scroll (4) is supported by the counterweight (8) through a second bearing (11), also known as an orbiting bearing (11), while the drive shaft (6) is supported by a first bearing (10), in particular a ball bearing (also known as a main bearing) (10), in the compressor housing (2). Within the compressor housing 2, a so-called counter pressure space 12 is formed behind the base plate 4a of the moving scroll 4. This counter pressure space 12, also called a counter pressure chamber, is subjected to a pressure that is lower than the outlet pressure (high pressure) but higher than the suction pressure (low pressure) of the substantially gaseous fluid being compressed. This counter pressure serves to press the moving scroll 4 against the fixed scroll 3.

[0021] The scroll compressor 1 further includes a guide device 13 that prevents rotation of the orbiting scroll 4 and allows circulation of the moving scroll 4. The guide device 13 is formed in a plurality of pocket-shaped receiving portions 14, each having a generally circular opening, on the rear surface of the base plate 4a of the moving scroll 4. These pocket-shaped receiving portions 14, also known as orbiting pockets, are arranged at a specific distance from each other and may be formed, for example, as closed holes. The guide device 13 also has pins 15 that protrude from a wall 16 of the compressor housing 2 and engage with one of the pocket-shaped receiving portions 14 formed in the base plate 4a of the moving scroll 4. Thus, a first end of the pin 15 can protrude from the wall 16 of the compressor housing 2, while a second end of the pin is embedded in the wall 16 of the compressor housing 2.

[0022] Due to the geometric design of the scroll compressor (1), there are many components in the counter-pressure space (12) that are subject to frictional stress. Therefore, in addition to the first bearing (10) as the main bearing and the second bearing (11) as the orbiting bearing, the scroll compressor (1) also has other components that are subject to circumferential frictional stress, such as the pocket-shaped receiving portion (14), that all require sufficient lubrication, especially during high-speed operation. Not only is the total amount of oil in the counter-pressure space (12) related to proper lubrication, but oil distribution is also important. Lubrication of the second orbiting bearing (11), which moves eccentrically and simultaneously rotates around the axis (9) of the moving scroll, is particularly challenging. However, sufficient lubrication of the orbiting bearing (11) is absolutely necessary to prevent bearing (11) fatigue.

[0023] FIG. 2 illustrates in detail a schematic representation of refrigerant flow and oil deposition in the counterpressure space (12) of the scroll compressor (1) illustrated in FIG. 1, without applying the substantial features of the present invention.

[0024] The function of the scroll compressor (1) primarily requires the return of gaseous refrigerant. In this way, passive lubrication of the second bearing (in this case, the ball bearing (11)) and surrounding friction-stress components by oil components in the refrigerant flow is also known. The rotational movement of the drive shaft (6) and counterweight (8) expels the oil necessary to lubricate the second orbiting ball bearing (11) and surrounding friction-stress components to the outside. In this way, the orbiting ball bearing and surrounding friction-stress components are in an internal area that is not circulated by the mixture of refrigerant gas and oil. Flow guides can result in oil vapor that does not flow through the second ball bearing (11) or surrounding friction-stress components and does not provide them with sufficient lubrication. Therefore, oil supply to the second ball bearing (11) cannot be guaranteed under all operating conditions, especially high-speed operation.

[0025] Referring to FIG. 2, a multiphase mixture of refrigerant gas and oil, the control mass flow (17), is first introduced into the swirl pocket (14). The refrigerant gas flow, still at high pressure before entering the counterpressure space (12), contains a low mass fraction of oil and enters the counterpressure space (12) through the counterpressure valve. The pressure of the refrigerant gas and oil mixture is reduced to a lower counterpressure level. The control mass flow (17) mixture exits the counterpressure space (12) through the first bearing (10) toward the low-pressure side (18). This ensures sufficient lubrication of the first bearing (10). During this process, oil continuously flows out of the counterpressure space (12). In normal operation, the complete mixture of refrigerant gas and oil entering the counterpressure space (12) is guided out of the counterpressure space (12) by the first bearing (10).

[0026] After the refrigerant gas and oil mixture of the control mass flow (17) enters the swirl pocket (14), the oil (19) is separated from the multiphase mixture of the control mass flow (17) by centrifugal force exerted by the rotational flow caused by the counterweight (8).

[0027] FIG. 3 illustrates in more detail the deposition effect of rotational flow without the use of a key feature of the present invention. A mixture of gaseous refrigerant and oil flows through the counterpressure space (12), specifically the cavity of the counterweight (8) and the second bearing (11). The fluid inlet (20) to the counterpressure space (12) is indicated by the first arrow in FIG. 3, and the fluid outlet (21) out of the counterpressure space (12) is indicated by the second arrow. A rotational flow is established in the cavity of the second bearing (11) and the counterweight (8). This flow results in the deposition of an oil phase (19) from the control mass flow (17) used to set the operating pressure, as shown diagrammatically in FIG. 3. The refrigerant and oil pass through the first bearing (10) and then exit the cavity. Thus, an oil layer (19) forms on the outer diameter of the counterpressure space (12). The thickness of this oil layer (19) is affected by the inner diameter of the outer ring (10a) of the first bearing (10). The low oil level 19a of oil collected by separation from the refrigerant gas / oil mixture (where this separation is the result of centrifugal force generated by the rotational flow caused by the rotating counterweight 8) is therefore sufficient to fill the counterpressure space 12 with oil 19 in the horizontal plane so that the outer ring 10a of the first bearing 10 is covered with oil, ensuring at least sufficient lubrication of the first bearing 10. However, this oil level 19a is not high enough to reach the second slewing bearing 11 and ensure lubrication there. This is because the oil 19 can only thicken until it reaches the lowest downstream diameter, which corresponds to the inner diameter of the outer ring 10a of the first bearing 10. Further thickening of the oil 19 in the counterpressure space cannot be achieved in this manner.

[0028] 4 illustrates a cross-sectional view of a first bearing 10 having a sealing washer 22 applied to one side thereof, which seals the radially outer portion of the first bearing area surrounded by the outer ring 10a and allows fluid to flow through it. The sealing washer 22 is fixed to the outer ring 10a of the first bearing 10 and is radially spaced apart from the inner ring 10b of the first bearing 10 so that the ring gap 23 between the sealing washer 22 and the inner ring 10b remains uncovered and the fluid mixture of refrigerant gas and oil can still flow therethrough.

[0029] FIG. 5 shows the condensation of the refrigerant gas and oil mixture in the counterpressure space 12, specifically in the cavity 12a of the second bearing 11 and counterweight 8, when a seal washer 22 is attached to one side of the first bearing 10. The seal washer 22 is attached to one side of the first bearing 10, facing the cavity of the counterweight 8 and the cavity of the second bearing 11. The ring-shaped seal washer 22 thus forms a barrier for the oil 19 deposited in the cavity. To overcome the seal washer 22, the oil 19 condenses in the cavity of the counterweight 8 and the cavity of the second bearing 11, as shown in FIG. 5. The set oil level 19b is determined by the inner diameter of the seal washer 22. The sealing washer (22) corresponds to a radial oil level (19b) that is set by the barrier effect of the application of the sealing washer (22), and its horizontal plane in the second bearing (11) has an inner diameter that is located between the outer ring (11a) and the inner ring (11b) of the second bearing (11), i.e., in the area of ​​the rolling element (11c) of the second bearing (11) that is formed in a ball shape. Therefore, the oil level (19b) of the oil (19) collected by separation from the refrigerant gas and oil mixture as a result of the centrifugal force of the rotating flow caused by the rotating counterweight (8) and further concentrated by the barrier effect of the ring-shaped sealing washer (22) is sufficient to fill the counterpressure space (12), in particular the cavity (12a) of the counterweight (8) and the cavity (12a) of the second bearing (11), with oil (19), so that the outer ring (11a) of the second bearing (11) is covered with oil (19) or even immersed in oil (19) to ensure sufficient lubrication of the second bearing (11) under all operating conditions.

[0030] 6A and 6B do not represent the complete invention, but serve to illustrate a specific, advantageous embodiment of the present invention. Both figures show perspective views of a conventional ball bearing used as a first bearing 10 for supporting a drive shaft 6 in a compressor housing 2. As with all rolling bearings, this ball bearing 10 has rolling elements 10c in the form of balls 10c distributed around the entire circumference of the ball bearing 10 between an inner ring 10b and an outer ring 10a to reduce frictional resistance. The drive shaft 6 has an eccentrically displaced connecting pin 24 for eccentrically driving the second bearing, molded, inserted, or fixed to its end face. This connecting pin 24 connects the drive shaft 6 to a counterweight (not shown), the axis of which corresponds to the axis of the moving scroll, not shown.

[0031] FIG. 6B illustrates a modified ball bearing (10) according to an advantageous embodiment of the present invention, in which a circumferential groove (25) is formed in the outer ring (10a) which serves to secure a ring-shaped sealing washer (not shown) to the first bearing (10).

[0032] Figure 7 is a perspective view of the drive shaft 6, which is integrated into the compressor housing 2 and has a connecting pin 24 supported by the first bearing 10, and the sealing washer 22 before being fixed to the first bearing 10. This drawing illustrates the first bearing 10 as a ball bearing 10 having an inner ring 10b, an outer ring 10a, and balls as rolling elements 10c. A circumferential groove 25 for the sealing washer 22, which is still inserted, is formed in the outer ring 10a. Figure 7 illustrates a portion of the compressor housing 2 that provides a counter-pressure space (not shown) with a cavity for a counterweight and a second bearing; other portions are not shown in Figure 7.

[0033] Figure 8 is also a perspective view of the drive shaft 6, which is integrated into the compressor housing 2 and has a connecting pin 24 supported by the first bearing 10. In contrast to the view in Figure 7, the seal washer is fixed to one side of the outer ring 10a of the first bearing 10. Therefore, the seal washer 22 applied to the first bearing 10 is also radially spaced from the inner ring 10b of the first bearing 10 so that the ring-shaped gap 23 between the seal washer 22 and the inner ring 10b remains uncovered so that refrigerant gas and oil fluids can still flow through the first bearing 10.

[0034] 9 is a cross-sectional view of the scroll compressor 1 taken along the plane of the sealing washer 22 secured to the first bearing 10. This cross-sectional view shows the compressor housing, the first bearing 10 having the outer ring 10a and the inner ring 10b, the drive shaft 6, and the connecting pin 24, in addition to the sealing washer 22. By securing the sealing washer 22 to the outer ring 10a, the sealing washer 22 seals the first bearing 10 on one side of the radially outer portion of the region between the outer ring 10a and the inner ring 10b of the first bearing 10, through which fluid can flow. At the same time, the sealing washer 22 is radially spaced from the inner ring 10b to maintain a ring-shaped gap 23 through which fluid can flow. [Explanation of symbols]

[0035] 1 Scroll compressor 2 Compressor housing 3 Fixed Scroll 3a Base Plate 3b Fixed Scroll Wall 4. Working scroll 4a Base Plate 4b Moving Scroll Wall 5 compression chambers 6 drive shaft 7 Rotation Axis 8 Balance weight 9. Axis of the moving scroll 10. First bearing, ball bearing 10a Outer ring of first bearing 10b Inner ring of first bearing 10c Rolling element, ball of first bearing 11 Second bearing 11a Outer ring of second bearing 11b Inner ring of second bearing 11c Rolling elements, balls of the first bearing 12 Counterpressure space 12a Second bearing and counterweight cavity 13 Guidance device 14 Pocket-shaped storage section, swivel pocket 15-pin 16 Compressor housing wall 17 Controlled Mass Flow 18 Low pressure side 19 Oil, oil layer, oil phase 19a Oil level (without seal washer) 19b Oil level (including seal washer) 20 Fluid inlet to counter pressure region 21 Fluid outlet from counter pressure space 22 Sealed Washer 23 Ring Gap 24 connecting pin 25 Circumferential groove

Claims

1. a compressor housing (2); a fixed scroll (3) fixed to the compressor housing (2); a movable scroll (4) movable in an eccentric manner on a circular path; a drive shaft (6) rotatable about a rotation axis (7); and a counterweight (8) rotatable together with the drive shaft (6), the movable scroll (4) being eccentrically connected to the drive shaft (6); a first bearing (10) that supports the drive shaft (6) in the compressor housing (2), a second bearing (11) that supports the movable scroll (4) in the balance weight (8), and a counter-pressure space (12) in the rear surface of the base plate (4a) of the movable scroll (4), which defines a cavity for the counterweight (8) and a cavity for the second bearing (11); Here, a sealing washer (22) is provided on one side of the region between the outer ring (10a) and the inner ring (10b) of the first bearing (10) through which a fluid can flow, sealing the first bearing (10) and maintaining a gap (23) through which a fluid can flow, The sealing washer (22) is ring-shaped with an inner diameter radially spaced from the inner ring (10b) of the first bearing (10) and is fixed to the outer ring (10a) of the first bearing (10); The scroll compressor, characterized in that the inner diameter of the sealing washer (22) corresponds axially between the outer ring (11a) of the second bearing (11) and the inner ring (11b) of the second bearing (11).

2. 2. The scroll compressor according to claim 1, wherein the sealing washer (22) and the gap (23) are formed in a ring-shaped manner.

3. 3. The scroll compressor according to claim 1, wherein the first bearing (10) is a rolling bearing (10) and is a ball bearing (10) having the outer ring (10a), the inner ring (10b), and rolling elements (10c) distributed over the entire circumference therebetween.

4. 4. The scroll compressor according to claim 3, wherein a circumferential groove (25) for clamping the sealing washer (22) is formed in the inner wall of the outer ring (10a) of the first bearing (10) to accommodate the sealing washer (22).

5. 2. The scroll compressor according to claim 1, wherein the second bearing (11) is a rolling bearing, that is, a ball bearing having an outer ring (11a), an inner ring (11b) and rolling elements (11c) distributed over the entire circumference therebetween.

6. 2. The scroll compressor according to claim 1, wherein during operation, a fluid mixture of refrigerant gas and oil flows into the counter-pressure space (12), and as a result of the centrifugal force of the rotational flow caused by the rotating counterweight (8) and additionally concentrated by the barrier effect of the ring-shaped sealing washer (22), the collected oil (19) separates from the mixture of refrigerant gas and oil, and the oil level (19b) fills the counter-pressure space (12), in particular the cavity of the counterweight (8) and the cavity of the second bearing (11), with the oil (19).

7. 7. The scroll compressor according to claim 6, wherein the horizontal plane of the radial oil level (19b) set by the barrier effect of the sealing washer (22) is between the outer ring (11a) of the second bearing (11) and the inner ring (11b) of the second bearing (11).

8. 8. The scroll compressor according to claim 7, wherein the horizontal plane of the radial oil level (19b) established by the barrier effect of the sealing washer (22) is closer to the inner ring (11b) of the second bearing (11) than to the outer ring (11a) of the second bearing (11).

9. The scroll compressor according to claim 1, characterized in that the gap (23) is provided between the sealing washer (22) and the inner ring (11b).

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